CN112855648B - Multi-redundancy shaft flow distribution servo valve - Google Patents

Multi-redundancy shaft flow distribution servo valve Download PDF

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Publication number
CN112855648B
CN112855648B CN202110308031.3A CN202110308031A CN112855648B CN 112855648 B CN112855648 B CN 112855648B CN 202110308031 A CN202110308031 A CN 202110308031A CN 112855648 B CN112855648 B CN 112855648B
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shaft
flow distribution
oil
shaft distribution
distribution valve
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CN112855648A (en
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何斌
张玄
訚耀保
李双路
郭文康
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Tongji University
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Tongji University
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/022—Flow-dividers; Priority valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/08—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only taps or cocks
    • F16K11/085—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only taps or cocks with cylindrical plug

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Multiple-Way Valves (AREA)
  • Servomotors (AREA)

Abstract

The invention relates to a multi-redundancy shaft flow distribution servo valve, which comprises a shaft flow distribution valve body stator, a shaft flow distribution valve sleeve and a shaft flow distribution valve core rotor, wherein the shaft flow distribution valve sleeve is arranged in a cold assembly mode, the shaft flow distribution valve core rotor is rotatably arranged in the shaft flow distribution valve sleeve, the shaft flow distribution servo valve is sequentially divided into three sealing areas which are not communicated with each other by a plurality of groups of sealing rings from top to bottom, the side wall of the shaft flow distribution valve stator is provided with i groups of working oil ports A/B, an oil supply port and an oil return port corresponding to three sealing areas respectively, the shaft flow distribution valve core rotor is provided with a plurality of oil supply channels and an oil return channel along the axial direction, and grooves and flow channels which are communicated with the oil supply channel and the oil return channel are respectively arranged in three sealing areas corresponding to the shaft distributing valve core rotor, wherein, part of the working oil ports are used as main working oil ports to be communicated with corresponding external actuating mechanisms, and the rest working oil ports are used as redundancy. Compared with the prior art, the invention has the advantages of shaft flow distribution, friction reduction, safety redundancy, continuity switching and the like.

Description

Multi-redundancy shaft flow distribution servo valve
Technical Field
The invention relates to the technical field of fluid control, in particular to a multi-redundancy shaft flow distribution servo valve.
Background
At present, the electro-hydraulic servo valves are in many kinds, and mainly include dual-nozzle flapper type electro-hydraulic servo valves, jet servo valves, direct-acting electro-hydraulic servo valves, electro-feedback electro-hydraulic servo valves, and moving-coil/moving-iron/single-nozzle electro-hydraulic servo valves. The nozzle baffle type electro-hydraulic servo valve is mainly characterized in that: the structure is simple, the manufacture is precise, the characteristics can be predicted, no dead zone and friction pair exist, the sensitivity is high, the inertia of the baffle is small, and the dynamic response is high; the defects are that the distance between the baffle and the nozzle is small, and the pollution resistance is poor; the jet servo valve is mainly characterized in that: the nozzle has large size, good pollution resistance, high volume efficiency, failure centering, high sensitivity and high resolution; the disadvantages are high processing difficulty and complex process.
The electro-hydraulic servo valve and the electro-hydraulic proportional valve are core elements of a hydraulic control system, the requirement on precision is high, detection and maintenance cost is improved, in the using process, due to the fact that pollution particles generated by pipelines, hydraulic elements, an actuating mechanism, a filtering device, a pump source, pressure impact in the system and the like cause abrasion of a valve core of the servo valve, the performance of the servo valve is poor, even the servo valve cannot work normally, if the problem that the abrasion servo valve needs to be replaced integrally or a redundant (standby) servo valve is solved, other parts of the abrasion servo valve except the valve core valve body have use values, and resource waste is caused.
In the aerospace and military fields, a multi-redundancy electro-hydraulic servo valve with high reliability usually adopts a multi-redundancy electric control part, the multi-redundancy design cannot solve the problem of mechanical abrasion of a pilot valve and a main valve core, and if a method that a plurality of servo valves are arranged on the same valve block and share an oil supply/return/working oil path channel is adopted, the influence of how to disconnect the abraded servo valve on an execution mechanism by replacing the servo valve also needs to be considered.
Disclosure of Invention
The present invention is directed to overcoming the above-mentioned deficiencies of the prior art and providing a multiple redundant axial flow servo valve.
The purpose of the invention can be realized by the following technical scheme:
a multi-redundancy shaft flow distribution servo valve comprises a shaft flow distribution valve body stator, a shaft flow distribution valve sleeve arranged in the shaft flow distribution valve body stator in a cold assembly mode and a shaft flow distribution valve core rotor rotatably arranged in the shaft flow distribution valve sleeve, wherein the shaft flow distribution servo valve is sequentially divided into three sealing areas which are not communicated by a plurality of groups of sealing rings from top to bottom, the side wall of the shaft flow distribution valve body stator is respectively provided with i groups of working oil ports A/B, an oil supply port and an oil return port corresponding to the three sealing areas, the shaft flow distribution valve core rotor is axially provided with a plurality of oil supply channels and an oil return channel, grooves and flow channels which are communicated with the oil supply channels and the oil return channels are respectively arranged in the three sealing areas corresponding to the shaft flow distribution valve core rotor, and part of the working oil ports are used as main working oil ports to be communicated with corresponding external actuating mechanisms, and the rest working oil ports are used as redundancy, the oil supply port and the oil return port are respectively communicated with an external oil source, and continuous proportional communication control between the oil supply channel and the oil return channel and the working oil ports A/B is respectively realized through the rotating shaft distributing valve core rotor, so that continuous different proportional speed control of an external actuating mechanism is realized.
And circular holes corresponding to the working oil port A/B, the oil supply port and the oil return port are respectively formed in the valve sleeve of the shaft flow distribution valve corresponding to the three sealing areas.
The oil return passage is positioned in the center of the shaft distributing valve core rotor, the depth of the oil return passage sequentially penetrates through the first sealing area and the second sealing area to reach the third sealing area, the oil return passage is communicated with the oil return port, the oil supply passages are uniformly arranged around the oil return passage respectively, and the depth of the oil supply passage penetrates through the first sealing area to reach the second sealing area, so that the oil supply passage is communicated with the oil supply port.
Each group of working oil ports A/B is arranged at a first horizontal setting position of a first sealing area, 2i grooves with the same structure are uniformly formed in the outer surface of the shaft distributing valve core rotor in the corresponding first sealing area along the circumferential direction, adjacent grooves are divided through non-grooved sections to be not mutually communicated, the centers of the grooves with odd numbers are communicated with corresponding oil supply channels through flow channels, the centers of the grooves with even numbers are communicated with the oil return channels at the centers through the flow channels, and the arc length and the axial size of each non-grooved section in the circumferential direction are larger than the bottom diameter of each working oil port, so that the working oil ports are blocked in the rotating process.
The axial flow distribution valve core rotor is expanded along the circumferential direction of the outer surface of the axial flow distribution valve core rotor, and the shape of each groove is formed by two triangles sharing the bottom edge, so that the width and the depth of each groove are gradually increased from two sides to the center.
The outer surface of the rotor of the shaft distributing valve core is provided with a groove in the corresponding second sealing area in the whole circumferential direction, so that the i oil supply channels are communicated with the oil supply port through the gap of the groove in the whole circumferential direction.
The outer surface of the shaft distributing valve core rotor is provided with a groove in the third sealing area in the whole circumferential direction, so that the central oil return channel is communicated with the oil return port through the gap of the groove in the whole circumferential direction.
The value of the group number i of the grooves is 4.
When the value of i is 4, at a first horizontal setting position of the first sealing area, 4 groups of working oil ports are sequentially arranged on the shaft flow distribution valve body stator at intervals of 45 degrees along the circumferential direction, the central angle range corresponding to each groove is 39 degrees, and the central angle corresponding to each non-grooved section is 6 degrees.
The adjusting range of the axial flow distribution servo valve is-90/i degrees to +90/i degrees, the axial flow distribution valve core rotor is driven by a servo motor or a stepping motor to rotate in the adjusting range, the continuous switching between the left, middle and right three-position functions is realized, and when one group of working oil ports has faults, the safe switching is completed by selecting any one of the other groups of working oil ports.
Compared with the prior art, the invention has the following advantages:
the invention breaks through the design concept of the conventional switch valve at present, realizes shaft flow distribution by adopting a form of slotting on a rotor shaft and a pair of oil supply channels P and oil return channels T, and effectively avoids the influence on the control performance caused by processing errors and assembly errors by arranging the valve sleeve of the shaft flow distribution valve in a cold assembly installation mode in the stator of the shaft flow distribution valve body.
And when the corresponding working oil port fails to work normally, the other group of the working oil ports can be directly selected as the redundancy to realize the safety switching function.
And thirdly, the invention realizes the reversing and orderly oil supply of the working oil port switch by a non-full-circumference slotting structure of the rotor in the circumferential direction, thereby realizing the logic flow distribution control of the actuating mechanism.
And fourthly, as the rotor and the stator of the axial flow distribution electromagnetic valve are in clearance fit, and a thrust bearing is adopted outside to reduce the rotation resistance moment of the rotor and the radial acting force generated when a large flow passes through.
And fifthly, no matter the axial distribution valve is in a working or non-working state, the rotor and the stator of the axial distribution valve are not in mechanical contact, so that the mechanical contact abrasion and eccentric wear hidden troubles between the rotor and the stator are reduced, and the long-term effective work of the axial distribution valve is ensured.
And sixthly, an axial flow distribution structure is adopted, the gap sealing length between the working oil port and the oil supply/return channel is realized, and the position matching of the groove and the hole in the valve sleeve is matched, so that the leakage amount is further reduced, and the circulation capacity is further increased.
Seventh, the invention can also realize the redundancy function of the electric control system by adding the coaxial servo motor.
Drawings
FIG. 1 is a schematic main sectional view (along the direction of opening) of the structure of the present invention.
Fig. 2 is a cross-sectional view of section I-I in fig. 1.
Fig. 3 is a cross-sectional view of section II-II in fig. 1.
Fig. 4 is a cross-sectional view of section III-III in fig. 1.
The notation in the figure is:
1. the shaft flow distribution proportional servo valve comprises a shaft flow distribution valve core rotor, a shaft flow distribution valve core rotor, a shaft flow rotor valve core rotor, a shaft rotor flow rotor valve core rotor, a shaft flow rotor valve core valve, a shaft rotor, a shaft flow distribution valve core, a shaft flow rotor, a shaft flow distribution valve core, a shaft flow rotor, a shaft flow distribution valve core, a shaft flow rotor, a shaft flow distribution valve core, a shaft flow rotor, a shaft valve core, a shaft flow distribution valve core, a shaft flow distribution valve core, a shaft flow distribution valve core, a shaft flow distribution valve core, a shaft flow valve core, a shaft flow distribution valve core, a shaft valve core, a shaft flow distribution valve core, a shaft flow valve core, a shaft flow valve core, a shaft flow valve core, a shaft.
Detailed Description
The invention is described in detail below with reference to the figures and specific embodiments.
Examples
As shown in fig. 1 to 4, the present invention provides a multi-redundancy shaft flow distribution servo valve, which includes an internal shaft flow distribution valve core rotor 2, a valve housing, and an external shaft flow distribution stator, wherein by adjusting the rotation of the axial flow distribution rotor to different angles, the working oil ports a/B are in continuous proportional communication with the oil supply port P0 and the oil return port T0, so as to realize continuous different-proportional speed control of the actuation of the actuator and redundant safety switching under fault conditions, the state of the actuator can be maintained unchanged within a specific rotation angle range, and when a certain group of working oil ports cannot work normally, the actuator can be directly switched to other groups of working oil ports to continue working.
The shaft flow distribution valve sleeve (4) and the shaft flow distribution valve stator (5) are subjected to cold assembly, and the stator sealing ring (6) is arranged at an inner hole groove of the shaft flow distribution valve stator (5) before the shaft flow distribution valve sleeve (4) is assembled;
the four stator sealing rings (6) are matched with the corresponding four rotor sealing rings (3) to form three separated sealing areas, and an oil return channel T and a plurality of oil supply channels P are formed in the center of the rotor of the shaft distribution valve core.
The first sealing area is specifically a range contained by the first rotor sealing ring 31 and the second rotor sealing ring 32, the first stator sealing ring 61 and the second stator sealing ring 62, and an oil return channel T and an oil supply channel P in the first sealing area are communicated with a plurality of groups of working oil ports under the rotation control;
the second sealing area is specifically a range contained by the space between the second rotor sealing ring 32 and the third rotor sealing ring 33 and the second stator sealing ring 62 and the third stator sealing ring 63, an oil supply channel P in the second sealing area is communicated with a plurality of groups of working oil ports under rotation control, and an oil return channel T is not communicated with the plurality of groups of working oil ports;
the third sealing area is specifically the range contained by the third rotor sealing ring 33 and the fourth rotor sealing ring 34, the third stator sealing ring 63 and the fourth stator sealing ring 64, the oil return channel T in the third sealing area is communicated with the multiple groups of working oil ports under rotation control, and the oil supply channel P is not communicated with the multiple groups of working oil ports.
The external oil supply port P0 is arranged on a second sealing area corresponding to the shaft distribution valve stator 5 and communicated with a plurality of oil supply channels P of the shaft distribution valve core rotor (2) through a groove on the outer surface of the shaft distribution valve core rotor (2) in the whole circumference of the second sealing area; the external oil return port T0 is arranged on a third sealing area corresponding to the shaft distribution valve stator 5 and is communicated with an oil return channel T of the shaft distribution valve core rotor (2) through a groove which is formed on the outer surface of the shaft distribution valve core rotor (2) in the third sealing area in the whole circumference;
as shown in fig. 2, taking I ═ 4 as an example, at a first horizontal setting position (I-I cross section) of the first sealing area, clockwise with the center line of the working oil port a1 as a reference, the outer surface of the shaft distribution valve core rotor (2) is respectively provided with a half groove gradually deepened and widened and a half groove gradually shallowly and narrowed between +3 ° to +22.5 ° and +22.5 ° to +42 °, the two half grooves are joined at the widest and deepest position to form a complete first groove, and the groove is communicated with the oil return channel T in the shaft distribution valve core rotor (2); a half groove with gradually increased depth and gradually increased width and a half groove with gradually decreased depth and gradually decreased width are respectively formed between-3 degrees to-22.5 degrees and-22.5 degrees to-42 degrees by taking the central line of the working oil port A1 as a reference in the counterclockwise direction, the two half grooves are combined at the widest and deepest part to form a complete second groove, and the groove is communicated with a corresponding oil supply channel P in the shaft distributing valve core rotor (2); the working oil port B1 is arranged in the middle of an ungrooved section at +42 degrees to +48 degrees;
similarly, the working oil port A2 of the shaft flow distribution servo valve is arranged at 90 degrees, a clockwise direction is taken as the reference of the central line of the working oil port A2, half grooves with gradually deepening and widening and half grooves with gradually shallowing and narrowing are respectively arranged between +3 degrees to +22.5 degrees and +22.5 degrees to +42 degrees on the shaft flow distribution valve core rotor (2), the two half grooves are combined at the widest and deepest part to form a complete third groove, and the grooves are communicated with an oil return channel T in the shaft flow distribution valve core rotor (2); with the central line of the working oil port A2 as a reference in the counterclockwise direction, respectively opening a half groove with gradually deepening and widening and a half groove with gradually shallowing and narrowing between-3 degrees to-22.5 degrees and-22.5 degrees to-42 degrees, wherein the two half grooves are combined at the widest and deepest part to form a complete fourth groove which is communicated with a corresponding oil supply channel P in the shaft flow distribution valve core rotor (2); the working oil port B2 is arranged in the middle of the ungrooved section of +132 degrees to +138 degrees;
the shaft flow distribution servo valve working oil port A3 is arranged at 180 degrees, a working oil port A3 center line is used as a reference for clockwise direction, half grooves with gradually deepened and gradually widened and half grooves with gradually shallowed and gradually narrowed are respectively arranged between +3 degrees to +22.5 degrees and +22.5 degrees to +42 degrees on the shaft flow distribution valve core rotor (2), the two half grooves are combined at the widest and deepest part to form a complete fifth groove, and the groove is communicated with an oil return channel T in the shaft flow distribution valve core rotor (2); with the central line of the working oil port A3 as a reference in the counterclockwise direction, respectively opening a half groove with gradually deepening and widening and a half groove with gradually shallowing and narrowing between-3 degrees to-22.5 degrees and-22.5 degrees to-42 degrees, wherein the two half grooves are combined at the widest and deepest part to form a complete sixth groove which is communicated with a corresponding oil supply channel P in the shaft flow distribution valve core rotor (2); the working oil port B3 is arranged in the middle of the ungrooved section from +222 degrees to +228 degrees;
the shaft flow distribution servo valve working oil port A4 is arranged at 270 degrees, a working oil port A4 center line is used as a reference for clockwise direction, half grooves with gradually deepened and gradually widened and half grooves with gradually shallowed and gradually narrowed are respectively arranged between +3 degrees to +22.5 degrees and +22.5 degrees to +42 degrees on the shaft flow distribution valve core rotor (2), the two half grooves are combined at the widest and deepest part to form a complete seventh groove, and the grooves are communicated with an oil return channel T in the shaft flow distribution valve core rotor (2); with the central line of the working oil port A4 as a reference in the counterclockwise direction, respectively opening a half groove with gradually deepening and widening and a half groove with gradually shallowing and narrowing between-3 degrees to-22.5 degrees and-22.5 degrees to-42 degrees, wherein the two half grooves are combined at the widest and deepest part to form a complete eighth groove which is communicated with a corresponding oil supply channel P in the shaft flow distribution valve core rotor (2); the working oil port B4 is arranged in the middle of an ungrooved section at +312 degrees to +318 degrees;
each groove is separated by the non-grooved section, and the arc length and the axial size of the non-grooved section in the circumferential direction are both larger than the bottom diameter of the working oil port A/B;
at a second horizontal setting position (section II-II) of the second sealing area, the shaft distribution valve core rotor (2) is communicated with an oil supply channel P on the shaft distribution valve core rotor (2) in a full-circumference grooving mode;
at a second horizontal setting position (III-III section) of the third sealing area, the shaft distribution valve core rotor (2) is communicated with an oil return channel T on the shaft distribution valve core rotor (2) in a full-circumference grooving mode;
the number of the openings in the middle of the shaft distribution valve core rotor (2) can be designed into one group to multiple groups of P, T channels according to the passing flow size, the switching frequency and the size of the shaft distribution valve core rotor (2).
The relative relationship of the related functions is illustrated by taking the following related angles as examples:
the continuous switching between the left, middle and right three-position functions of the multi-redundancy shaft flow distribution servo valve is realized by adjusting the servo motor to rotate between minus 22.5 degrees and plus 22.5 degrees (when i is equal to 4),
the +/-3-degree range corresponds to the median function, and 0 covers the zero position;
the left end position P-Ai/Bi-T of the multi-redundancy shaft flow distribution servo valve is corresponding to +3 degrees to +22.5 degrees;
right end position P-Bi/Ai-T of multi-redundancy shaft flow distribution servo valve corresponding to-3 degrees to-22.5 degrees
The corresponding seal segments are within +/-3 deg..
If a corresponding group of working oil ports A1& B1 have faults and cannot work normally, another group of Ai & Bi, i is not equal to 1, i is 2, 3 and 4 can be directly selected, and therefore the safety switching function is achieved.
The actual relevant angle and the axial distribution valve neutral position function can design and adjust the mutual corresponding angle relation according to the requirement, the specific corresponding angle is communicated or disconnected with the oil supply port P0 and the oil return port T0 through the groove of the distribution shaft in the working oil port area, the continuous switching of the oil supply flow of the working oil ports Ai/Bi is realized, and the control of the action of the actuating mechanism is realized.

Claims (10)

1.一种多冗余的轴配流伺服阀，其特征在于，包括轴配流阀体定子(5)、通过冷装配的方式安装在轴配流阀体定子(5)内的轴配流阀阀套(4)以及可旋转地安装在轴配流阀阀套(4)内的轴配流阀芯转子(2)，该轴配流伺服阀由上至下由多组密封圈依次分割为互不连通的三个密封区域，所述的轴配流阀体定子(5)侧壁上对应三个密封区域分别开设i组工作油口A/B、一个供油口(P0)以及一个回油口(T0)，i＝2、3或4，所述的轴配流阀芯转子(2)沿轴向开设多个供油通道(P)和一个回油通道(T)，并且在轴配流阀芯转子(2)对应三个密封区域内分别设置用以与供油通道(P)和回油通道(T)连通的沟槽和流道，其中部分工作油口作为主工作油口与对应的外部执行机构连通，其余的工作油口作为冗余，供油口(P0)和回油口(T0)分别与外部油源连通，通过转动轴配流阀芯转子(2)，分别实现供油通道(P)和回油通道(T)分别与工作油口A/B之间的连续比例连通控制，进而实现外部执行机构的连续不同比例速度控制。1. A multi-redundant shaft distribution servo valve, characterized in that it comprises a shaft distribution valve body stator (5), a shaft distribution valve sleeve (5) installed in the shaft distribution valve body stator (5) by cold assembly 4) and the shaft distribution valve core rotor (2) rotatably installed in the shaft distribution valve sleeve (4), the shaft distribution servo valve is divided into three groups of sealing rings that are not connected to each other from top to bottom. In the sealing area, the side walls of the shaft distribution valve body stator (5) correspond to the three sealing areas respectively with i groups of working oil ports A/B, an oil supply port (P0) and an oil return port (T0), i = 2, 3 or 4, the shaft distribution valve core rotor (2) is provided with a plurality of oil supply channels (P) and an oil return channel (T) in the axial direction, and the shaft distribution valve core rotor (2) corresponds to The three sealing areas are respectively provided with grooves and flow channels for communicating with the oil supply channel (P) and the oil return channel (T). The oil supply port (P0) and the oil return port (T0) are connected to the external oil source respectively. By rotating the shaft distribution valve core rotor (2), the oil supply channel (P) and oil return are realized respectively. The continuous proportional communication control between the channel (T) and the working oil ports A/B respectively, thereby realizing the continuous different proportional speed control of the external actuator. 2.根据权利要求1所述的一种多冗余的轴配流伺服阀，其特征在于，所述的轴配流阀阀套(4)上对应三个密封区域分别开设与工作油口A/B、供油口(P0)以及回油口(T0)对应的圆孔。2 . The multi-redundant shaft distribution servo valve according to claim 1 , wherein the corresponding three sealing areas on the shaft distribution valve sleeve (4) are respectively provided with working oil ports A/B. 3 . , the round holes corresponding to the oil supply port (P0) and the oil return port (T0). 3.根据权利要求2所述的一种多冗余的轴配流伺服阀，其特征在于，所述的回油通道(T)位于轴配流阀芯转子(2)的中心处，其深度依次穿过第一密封区域和第二密封区域到达第三密封区域，实现与回油口(T0)的连通，所述的多个供油通道(P)分别均匀开设在回油通道(T)周围，其深度穿过第一密封区域到达第二密封区域，实现与供油口(P0)的连通。3. The multi-redundant shaft distribution servo valve according to claim 2, characterized in that, the oil return channel (T) is located at the center of the shaft distribution valve core rotor (2), and its depth passes through in sequence Through the first sealing area and the second sealing area to reach the third sealing area, the communication with the oil return port (T0) is realized, and the plurality of oil supply channels (P) are evenly opened around the oil return channel (T), respectively, Its depth passes through the first sealing area to the second sealing area, achieving communication with the oil supply port (P0). 4.根据权利要求3所述的一种多冗余的轴配流伺服阀，其特征在于，每组工作油口A/B设置在第一密封区域的第一水平设定位置处，并且轴配流阀芯转子(2)外表面在对应第一密封区域内沿周向均匀开设结构相同的2i个沟槽，相邻沟槽间通过未开槽区段分割使得不互相连通，其中，奇数序号的沟槽的中心与对应的供油通道(P)通过流道连通，偶数序号的沟槽的中心均与中心的回油通道(T)通过流道连通，每个未开槽区段在圆周方向弧长及轴向尺寸均大于工作油口的底径，用以实现转动过程中对工作油口的封堵。4. A multi-redundant shaft distribution servo valve according to claim 3, characterized in that, each group of working oil ports A/B is set at the first horizontal setting position of the first sealing area, and the shaft distribution is The outer surface of the spool rotor (2) is uniformly provided with 2i grooves with the same structure in the circumferential direction in the corresponding first sealing area, and the adjacent grooves are divided by unslotted sections so that they are not connected to each other. The center of the groove is communicated with the corresponding oil supply channel (P) through the flow channel, the center of the even-numbered groove is connected with the central oil return channel (T) through the flow channel, and each unslotted section is in the circumferential direction. Both the arc length and the axial dimension are larger than the bottom diameter of the working oil port, so as to realize the blocking of the working oil port during the rotation process. 5.根据权利要求4所述的一种多冗余的轴配流伺服阀，其特征在于，沿轴配流阀芯转子(2)外表面周向展开，每个沟槽的形状均由两个共底边的三角形组成，使得每个沟槽的宽度和深度由两边向中心逐渐增大。5. A multi-redundant axial flow distribution servo valve according to claim 4, characterized in that, along the outer surface of the axial flow distribution valve core rotor (2) circumferentially developed, the shape of each groove is formed by two common The bottom side of the triangle is formed, so that the width and depth of each groove gradually increase from the two sides to the center. 6.根据权利要求3所述的一种多冗余的轴配流伺服阀，其特征在于，所述的轴配流阀芯转子(2)外表面在对应第二密封区域内全周向开槽，使得i个供油通道(P)通过全周向开槽的间隙与供油口(P0)连通。6 . The multi-redundant shaft distribution servo valve according to claim 3 , wherein the outer surface of the shaft distribution valve core rotor ( 2 ) is fully circumferentially grooved in the corresponding second sealing area, so that i 6 . Each of the oil supply passages (P) communicates with the oil supply port (P0) through the gaps grooved in the entire circumference. 7.根据权利要求3所述的一种多冗余的轴配流伺服阀，其特征在于，所述的轴配流阀芯转子(2)外表面在对应第三密封区域内全周向开槽，使得中心的回油通道(T)通过全周向开槽的间隙与回油口(T0)连通。7 . The multi-redundant shaft distribution servo valve according to claim 3 , wherein the outer surface of the shaft distribution valve core rotor ( 2 ) is fully circumferentially grooved in the corresponding third sealing area, so that the center The oil return passage (T) of the 1000L is communicated with the oil return port (T0) through the full circumferentially slotted gap. 8.根据权利要求4所述的一种多冗余的轴配流伺服阀，其特征在于，所述的沟槽的组数i的取值为4。8 . The multi-redundant shaft distribution servo valve according to claim 4 , wherein the value i of the group number i of the grooves is 4. 9 . 9.根据权利要求8所述的一种多冗余的轴配流伺服阀，其特征在于，当i的取值为4时，在第一密封区域的第一水平设定位置处，4组工作油口在轴配流阀体定子(5)上沿周向每隔45°依次设置，每个沟槽对应的圆心角范围为39°，每个未开槽区段对应的圆心角为6°。9 . The multi-redundant shaft distribution servo valve according to claim 8 , wherein when the value of i is 4, at the first horizontal setting position of the first sealing area, 4 groups of working The oil ports are arranged on the stator (5) of the shaft distribution valve body in sequence at intervals of 45° in the circumferential direction, the central angle corresponding to each groove is 39°, and the central angle corresponding to each unslotted section is 6°. 10.根据权利要求1所述的一种多冗余的轴配流伺服阀，其特征在于，该轴配流伺服阀的调节范围为-90/i°～+90/i°，当轴配流阀芯转子(2)通过伺服电机或步进电机驱动在调节范围内转动，实现左中右三位机能之间的连续切换，当出现一组工作油口故障时，通过选择到其余任一组工作油口完成安全切换。10. The multi-redundant shaft distribution servo valve according to claim 1, wherein the adjustment range of the shaft distribution servo valve is -90/i°～+90/i°, when the shaft distribution valve core The rotor (2) is driven by a servo motor or a stepping motor to rotate within the adjustment range to achieve continuous switching between the three functions of the left, middle and right. When a group of working oil ports fails, select any other group of working oil The port completes the safe switch.
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